Transmission for vehicles



Feb. 27, 1962 J. P. SIMON TRANSMISSION FOR VEHICLES 3 Sheets-Sheet 1Original Filed Oct. 18, 1956 & 8 1 2 7 f /M 2 V //AQ .3 iw Wu 2 I 0% j MA ll. m 67 ll 1 42611 625 2 2 222 4 \I I. 8 lll ////////W Feb. 27, 1962J. P. SIMON TRANSMISSION FOR VEHICLES Original Filed Oct. 18, 1956 3Sheets-Sheet 2 l 27/ 72 #07: km 1? Simon Feb. 27, 1962 J. P. SIMONTRANSMISSION FOR VEHICLES Original Filed Oct. 18, 1956 5 Sheets-Sheet 3United States Patent 3,022,683 TRANSMISSION FOR VEHICLES John P. Simon,Glen Ellyn, I]l.,'assignor to International Harvester Company, acorporation of New Jersey Continuation of application Ser. No. 616,829,Oct. 18, 1956. This application Mar. 30, 1959, Ser. No. 803,050

14 Claims. (Cl. 74-759) This invention relates to transmissions and isprimarily concerned with a transmission for vehicles. This applicationis a continuation of my application Serial No. 616,829 filed October 18,1956, now abandoned.

An object of the invention is to provide -a transmission having lowrotational speeds of moving parts.

Another object of the invention is to provide a transmission havingsimilar forward and reverse output shaft speeds.

A further object of the invention is to provide a transmission having agreater variation of speeds of the output shaft than transmissions usedin the past.

A still further object of the invention is to provide a transmissionwherein there can be obtained a two to one ratio of input shaft speed tooutput shaft speed using planetary gearing.

The foregoing and other objects of the invention will be apparent fromthe construction and arrangement illustrated in the accompanyingdrawings wherein:

FIGURE 1 is a cross sectional view through one form of the transmissionof the present invention,

FIGURE 2 is a cross sectional view taken on the line 2-2 of FIGURE 1,

FIGURE 3 is a cross sectional view taken on the line 33 of FIGURE 1,

FIGURE 4 is a cross sectional view taken on the line 44 of FiGURE 1,

FIGURE 5 is a cross sectional view through a modified form oftransmission, and

FIGURE 6 is a cross sectional view taken on the line 66 of FIGURE 5.

The invention proposes an improved transmission. The transmission iscomprised of a casing and an input shaft operatively connected to asource of power and an output shaft and a gear fixedly secured on theinput shaft and a gear fixedly secured on the output shaft and a gearrotatably mounted on the output shaft. A first planetary gear set mesheswith the gear on the input shaft and a second planetary gear set mesheswith the gear fixedly secured on the output shaft and a third planetarygear set meshes with the gear rotatably mounted on the output shaft. Aclutch is mounted between the first, second and third planetary gearsets and the input shaft. A pair of brakes are mounted between thefirst, second and third planetary gear sets and the casing and a thirdbrake is mounted between the gear rotatably mounted on the output shaftand the casing. This transmission has the advantages of similar forwardand reverse output shaft speeds and low rotational speeds of movingparts and a greater variation of speeds of the output shaft. With thistransmission it is possible to obtain a two to one ratio of input shaftspeed to output shaft speed using planetary gearing.

in the drawings referring first to FIGURES l to 4 inclusive 10 generallydesignates a transmission for 2. ve-

'hicle such as a tractor or highway truck. The transice mission 10 iscomprised of a casing 11 and an input shaft 12 is rotatably mounted onbearings in the casing and is operatively connected to a source of powersuch as the engine of the tractor or truck. An output shaft 13 isrotatably mounted on hearings in the casing 11 in end to end spacedrelation with respect to the input shaft 12. A spur gear 14 having 26teeth is formed integral with the input shaft 12. A carrier 15 isdisposed in the casing 11 adjacent the adjacent ends of the input andoutput shafts 12 and 13 and another carrier 16 is fixedly secured on theoutput shaft. A spur gear 17 having 26 teeth is formed integral with theend of the output shaft 13 and a spur gear or sun gear 18 having 24teeth is rotatably mounted on bearings on the output shaft between thecarrier 16 and the casing 11. An orbit wheel 19 is disposed in thecasing 11 and has three spaced sets of internal gear teeth 20, 21 and22. Each of the sets 21) and 21 has 88 teeth and set 22 has teeth. Aplu-. rality of spur gears 23 each having 31 teeth are rotatably mountedon the carrier 15 and mesh with the gear 14 on the input shaft and theset of teeth 20 on the orbit wheel. A plurality of spur gears 24 eachhaving'29 teeth are rotatably mounted on the carrier 15 and mesh withthe gear 17 on the output shaft and a plurality of spur gears 25 eachhaving 29 teeth are rotatably mounted on the carrier and mesh with thegears 24 and the set of teeth 21 on the orbit wheel. A plurality of spurgears 26 each having 18 teeth are rotatably mounted on the carrier 16and mesh with the gear 18 on the output shaft and the set of teeth zz onthe orbit wheel. A clutch 27 is disposed between the input shaft and thecarrier 15. A brake 23 is mounted between the carrier 15 and the casing11 and a brake 2% is mounted between the orbit Wheel 19 and the casingand a brake 311 is mounted between the gear 10 and the casing 11. Thistransmission has two speeds forward and two speeds reverse.

The operation of the transmission shown in FIGURES 1 to 4 inclusive isas follows: With only the brake 28 engaged and brakes 29, 30, and clutch27 disengaged, the carrier 15 is held stationary and gear 14 drivesthrough idler gears'23 to rotate orbit wheel 19. The set of teeth 21 onorbit wheel 19 drives gear 17 and the output shaft through gears 24 and25. Gears 18 and 26 and the set of teeth 22 on the orbit wheel are idle.The rotation of the output shaft 13 is in a direction reverse of therotation of the input shaft 12. With the brake 29 engaged and brakes 23,3t and clutch 27 disengaged, the orbit wheel 19is held stationary. Gear14 drives gears 23 around the set of teeth 20 moving carrier 15 causinggears 25 to revolve around the set of teeth 21 and drive gear 17 and theoutput shaft through gears 24. Gears 18, 26 and the set of teeth 22 areidle. The rotation ofthe output shaft is in a direction reverse of therotation of the input shaft. With the clutch 27 engaged and brakes 28,29 and 30 disengaged, the carrier 15 is locked to the input shaft 12thereby locking all gears in all planetaries to the input shaft. Theoutput shaft 13: rotates the same speed and in the same direction as theinput shaft 12. With the brake 30 engaged and brakes 28, 29, and clutch27 disengaged, gear 18 is held stationary and carrier 16 drives gears 26around gear 18 overdriving the orbit wheel 19. Rotation of the orbitwheel19 together with rotation of gear 14 causes coincident rotation ofcarrier 15 driving gears 25 around inside of movgreater diameter thansaid driving sun gear.

ing orbit wheel 'H and driving gear '17 and the output shaft '13 throughgears "24. -The rotation of the output shaft 13 is then partlyregenerated through the planetary gear set 18, 22, .26. The regenerativeaction provides additional speed reducing effect. The rotation of theoutput shaft is in the same direction as the rotation of the inputshaft. Comprehension of the rather complex gear train which is inoperation for obtaining this forward reduced drive connection may befacilitated by considering firstthe condition that would prevail if thering wheel 19 were somehow caused to rotate at the same speed as thedriving sun gear 14. Under this assumed condition the planet gears 23would not rotate about their axes, the carrier 15 would be rotated atthe same speed as the driving sun gear 14 and as the ring wheel 19 andtherefore the idler planet gears 25 would be revolved about the carrieraxis'but would be held against rotation about their own axes and wouldconstrain the idler planet gears 24 against rotation about their ownaxes so that .as they are carried'by the rotating carrier to'revolveabout the carrier axis these gears24. act as keys to cause. the drivensun gear 17 to rotate at carrier speed. 'Thus if the ring wheel19 wererotated at the same forward speed as the driving sun gear 14 there wouldbe a condition tantamount to the carrier 15 and planetary gear setsassociated therewith being locked up so all elements of these planetarygear sets have no relative movement and rotate as a unit about thecommon axis of theshafts 12 and 13. If, while said elements are thusrotating as a unit, the ring wheel 19 were to be rotated at .some fasterspeed while the driving sun gear 14 continued at the same speed, thering Wheel 19 would rotate at an overspeed relative to the carrier 15.This would cause the ring gear 20 to rotate the planet gears 23reactively against the driving sun gear .14 to rotate the carrier 15forwardly at an overspeed less than that of the ring wheel 19 relativelyto the driving sun gear because of the gear 20 having Concurrently, thering gear 21 would continue to rotate faster than the carrier 15 andthis relative rotation of the ring gear 21 and the carrier'would causesuch ring gear to be efiective through the planet idler gears 25 and 24to rotate the driven sun gear 17 at an underspeed relatively to thecarrier that exceeds the overspeed of ring gear 21 relatively to thecarrier because of the ringgear having more teeth than the driven sungear. 'I'he'net effect of the overspeed ring 19 causing some increase inspeed of the -carrier 15 over the speed of driving sun gear '14 anddiminution in speed of the driven sun gear 17 greater than the speedincrease of the carrier 15 is to cause this driven sun gear to be drivenat diminished speed with respect to the drive. gear 14 and drive shaft12. 'The .amount of this speed reduction of the driven sun gear and ofthe driven shaft 13 is a direct function of the overspeed of the ringwheel 19, which overspeed, in the present case, is determined by therelative diameter of the sun gear 18 and ring gear 22 of the planetarygear train 18, 2'6, 22 for driving the ring wheel 19 at an overspeedfrom the driven shaft 13.

=A modified form of transmission having two speeds forward and twospeeds reverse isshown lILFIGURES 5 and 6. The transmission is the sameas that shown in FIGURES 1 to 4 inclusiveexcept that the shapeof thecasing has been changed and the brake 50 'has been :shifted to adifferent position and a gear set has been added. The modifiedtransmission has a casing 31 and :an orbit wheel 32having internal gearteeth 33 and a rpluralityof spur gears '34, are rotatably mounted on thecasing and mesh with the orbit wheel and the gear 18 w and a brake 35 ismounted between theorbit wheel and ithe casing. The orbitwheel 32 hasgear teeth and each gear34 has .18 teeth. The operation ofthisztransmission with the clutch 2'7 and brakes 28 and 29 engaged "isthe same as for the first form o'f transmission and engagement-of brake35 holds orbitwheel'm, #gears '34 Ratio of output shaft Rpm. of Clutchor brake engaged speed to inoutput shaft put shaft speed Brake 30 a V.47 750 Clutch 27 1.0 l (300 Burke 29. -.54' l -s65 Brake 2s 1.0 1 -1,600

1 Thenegative sign represents rpm. in the reverse direction,

These transmissions have a greater variation of speeds of the output.shaft because the planetary gear sets 14, 23 and 18, 26 can easily bechanged. With'this transmis sion it is possible to .obtain a two to oneratio of input shaft speed to output shaft speed using planetary gearingas can be seen from the table. These transmissions provide similarforward and reverse output shaft speeds as can also be seen from thetable.

Each output shaft speed selected requires .the engage mentof only onedrive effecting element, i.e. a clutch or brake in contrast tothe usualtwo drive effecting elements concurrently. This simplifies the valveused for control of the transmission .and reduces the shift shock oftencaused by two drive effecting elements coming into or going out ofengagement.

What i is claimed is:

l. A transmission comprising a casing, an input shaft rotatably .mountedin .the casing vand operatively connected to a source of power, anoutput shaft rotatably mounted in the casing in longitudinally alignedrelation with the input shaft, a gear with external teeth fixedlysecured on the input shaft, a gear with external teeth fixedly securedon the output shaft, a gear rotatably mounted on the output shaft, afirst planetary gear set having a planet gear meshing with .the gear onthe input shaft, a second planetary gear set having a planet gearmeshing withtthe gear fixedly secured on the output shaft, said firstand second gear sets havinga common carrier, a third planetaryvgearset.meshing with the gear rotatably mounted on the output shaft, ring gearsoperatively connected to the planettgears of the first, second and thirdgear sets, means including a clutch operatively con- .nected betweenthecarrier of the first and second planetary gear sets and theinput shaft,a first brake operative between the carrier andthe casing, .a secondbrake operative between the ring gears and the casing, and meanscomprising a brake operative between the gear rotatably mounted on theoutput shaft and .the casing.

2.. A transmission comprising acasing, aninput shaft rotatably mountedin .the casing .and operatively .connected to a source of power, anoutput shaft rotatably mounted in the casingin end to end spacedrelation with 'the input shaft, a spur gear fixedly secured on the inputshaft, a first carrier disposed in the .casing adjacent said ends of theinput and output shafts, a second carrier fixedly secured on the outputshaft, a spur gear fixedly secured on said end of the output shaft, aspur gear rotatably mounted on the goutputshaft between the secondcarrier and the casing, an orbit wheel disposed in the easing and havinga first .and second and a third set of internal teeth arranged in spacedrelation, a first plurality of spurgears rotatably mounted on thefirstcarrier and meshingwith the. gear on the input shaft and the first setof teeth on .the orbit wheel, a second plurality of spur gears rotatablymounted on the first carrier andxmeshing with the gear fixedly securedon the output shaft, a third plurality of spur gears rotatably mountedon the first carrier and meshing with the second plurality of spur gearsand the second set of teeth on the orbit wheel, a fourth plurality ofspur gears rotatably mounted on the second carrier and meshing with thegear rotatably mounted on the output shaft and the third set of teeth onthe orbit wheel, a clutch drivingly connectible between the input shaftand the first carrier, a first brake operatively connectible between thefirst carrier and the casing, a second brake operatively connectiblebetween the orbit wheel and the casing, and a third brake operative tostop rotation of the gear rotatably mounted on the output shaft.

3. A transmission comprising a casing, an input shaft rotatably mountedin the casing and operatively connected to a source of power, an outputshaft rotatably mounted in the casing in end to end spaced relation withthe input shaft, a spur gear fixedly secured on the input shaft, a firstcarrier disposed in the casing adjacent said ends of the input andoutput shafts, a second carrier fixedly secured on the output shaft, aspur gear fixedly secured on said end of the output shaft, a spur gearrotatably mounted on the output shaft between the second carrier and thecasing, a first orbit wheel disposed in the casing and having a firstand a second and a third set of internal teeth arranged in spacedrelation, a first plurality of spur gears rotatably mounted on the firstcarrier and meshing with the gear on the input shaft and the first setof teeth on the first orbit wheel, a second plurality of spur gearsrotatably mounted on the first carrier and meshing with the gear fixedlysecured on the output shaft, a third plurality of spur gears rotatablymounted on the first carrier and meshing with the second plurality ofspur gears and the second set of teeth on the first orbit wheel, afourth plurality of spur gears rotatably mounted on the second carrierand meshing with the gear rotatably mounted on the output shaft and thethird set of teeth on the first orbit wheel, a second orbit wheeldisposed in the casing and having a set of internal teeth, a fifthplurality of spur gears rotatably mounted on the casing and meshing withthe gear rotatably mounted on the output shaft and the teeth on thesecond orbit wheel, a clutch drivingly connectible between the inputshaft and the first carrier, a first brake operatively connectiblebetween the first carrier and the casing, a second brake operativelyconnectible between the first orbit wheel and the casing, and a thirdbrake operatively connectible between the second orbit wheel and thecasing.

4. In a speed reduction driving connection between a pair of shafts, sungears respectively fixed for rotation with said shafts, ring gearsrespectively complemental with said sun gears and interconnected forrotation in unison, a carrier structure, a first set of planet gearsjournalled for rotation on the carrier structure and meshing with one ofthe sun gears fixed to one of said shafts and also meshing with the ringgear complemental thereto, a planetary idler gear journalled upon thecarrier structure and meshing with the other sun gear in drivingrelation therewith, a second planetary idler gear journalled upon thecarrier structure and meshing with the first planetary idler gear andalso with the ring gear complemental to said other sun gear, selectivelybraked reaction means and means driven by the other shaft and thereaction means and drivingly connected with the ring gears to effectrotation thereof in the same direction as said other shaft is driven.

5. The combination set forth in claim 4 wherein the means for drivingthe ring gears constitutes gear means for driving the ring gears at anoverspeed with respect to said other shaft.

6. The combination set forth in claim 4 wherein the reaction meanscomprises a sun gear and the means for driving the ring gears from saidother shaft comprises a carrier constrained for rotation with said othershaft, planet gears journalled upon such carrier and meshing with saidlast mentioned sun gear and a ring'gear meshing with the planet gearsand drivingly connected with said ring gears.

7. The combination set forth in claim 4 wherein the reaction meanscomprises a sun gear, and means for driving the ring gears constitutesgear means for driving the ring gears at an overspeed with respect tosaid other shaft and brake means for preventing rotation of said lastnamed sun gear.

8. In a change speed transmission between a pair of shafts and having acasing, sun gears respectively fixed for rotation with said shafts, ringgears respectively complemental with said sun gears and interconnectedfor rotation in unison, a carrier structure, a first set of planet gearsjournalled for rotation on the carrier structure and meshing with one ofthe sun gears fixed to one of said shafts and also meshing with the ringgear complemental thereto, a planetary idler gear journalled upon thecarrier structure and meshing with the other sun gear in drivingrelation therewith, a second planetary idler gear journalled upon thecarrier structure and meshing with the first planetary idler gear andalso with the ring gear complemental to said other sun gear, a furthersun gear and means driven by the other shaft and drivingiy connectiblewith the further sun gear and the ring gears, brake means forselectively connecting said last named sun gear to the casing and brakemeans for alternatively connecting the ring gears to the casing.

9. The combination set forth in claim 8 wherein there is also brakemeans for selectively connecting the carrier structure to the casingwhen the other two brake means are disengaged.

10. The combination set forth in claim 9 wherein there is a clutchselectively operable to connect the said carrier with the one shaft whenall three brake means are disengaged.

11. In a transmission having input and output shafts, each of saidshafts having a sun gear constrained for rotation therewith, ring gearscomplemental with said sun gears, compounded planetary gearing includinga first pinion meshing with the sun gear on the input shaft and the ringgear complemental thereto and a second pinion meshing with the sun gearon the output shaft and a third pinion meshing with the second pinionand the ring gear complemental thereto, and a carrier structure mountingthe said pinions, a gear rotatably mounted on the ouput shaft, firstmeans operatively connected with the ring gears and the gear rotatablymounted on the shaft, second means including a clutch operative betweenthe carrier and the input shaft, and brake means selectively operativeto brake the carrier, the ring gears, and the gear rotatably mounted onthe shaft.

12. The invention according to claim 11 and said brake means cooperativewith said gear rotatably mounted on the output shaft comprising a pinionmeshing with said last named gear, a ring gear meshing with said pinionand a brake for preventing rotation of the ring gear.

13. The invention according to claim 11 and said first means including acarrier constrained for rotation with the output shaft and planet gearsjournalled upon said last named carrier and meshing with the gearrotatably mounted on the output shaft and a ring gear meshing with theplanet gears and drivingly connected with said ring gears.

14. A transmission comprising a casing and input shaft rotatably mountedin the casing and operatively connected to a source of power, an outputshaft rotatably mounted in the casing, a gear fixedly secured on theinput shaft, a gear fixedly secured on the output shaft, a gearrotatably mounted on the output shaft, a first planetary gear set havinga planet gear meshing with the gear on the input shaft, a secondplanetary gear set having a planet gear meshing with the gear fixedlysecured on the output shaft, said first and second gear sets having acommon 7 r 8 carrier, said output shaft including means carrying a thering gears and the casing, :and means comprising a third planetary gearset having :a planet gear meshing brake operative betweenthe casingandihe-gear rotatably with the gear rotatably mounted on the outputshaft, mounted .onthe outputshaft. a ring gears roperat'iv'ely connectedto the planet gears of the first and third gear sets, means meshing thegear of 5 References Cited in the file fififhi paten the second gear-setwith the ring gears, means including UNITED STATES A aiciutchoperatively connected between the carrier and a the input vshaft,vafirsthrake operative between the -car- 2580891 Clerk rier and thecasing, a second brake operative between Langdon "''J"" 1959

